Apparatus for rolling disks



May 21, 1963 M. D. STONE ETAL APPARATUS FOR ROLLING DIsKs 5 Sheets-Sheet 1 Filed Jan. 16, 1959 Awb N umm d2 om 2. dm m m H m M l T 0 E 0 AP@ n 0L m T m W M 5 H l 0.0/ 6H w DHA on W ww NQ Qmm dm di :zu 1 L nl |r||||||L lllmnulrm d.. nldmw- NIMH I Hl l I\ -3| -IIL f .Q E I dw@ @E May 2l, 1963 M. D. STONE ETAL APPARATUS FOR ROLLING DISKS 5 Sheets-Sheet Filed Jan. 16, 1959 nvm n. n. im 5m 9 HOWARD TALBOT THE/R ATTORNEY May 21, 1963 M. D. sToNE ETAL APPARATUS FOR ROLLING DISKS Filed Jan. 16, 1959 5 Sheets-Sheet 5 MORE/S D. S TONE HOWARD H. TALBOT i THE/? ATTRNEY May 21, 1963 M. D. STONE ETAL APPARATUS FoR ROLLING DIsKs 5 Sheets-Sheet 4 Filed Jan. 16, 1959 /NVENTORS n l Ew.. m TAW 5. H @HMH H Rm y OO B MH` May 21, 1963 M. D. STONE ETAL 3,090,264

APPARATUS FOR ROLLING DISKS Filed Jan. 16, 1959 5 Sheets-Sheet 5 FIG. I2

FIG.I5

/lV VE /V TORS MOR/W5 D. S TONE HOWARD H. TALBOT THE/H ATTORNEY United States Patent O 3,090,264 APPARATUS FOR ROLLlNG DISKS Morris D. Stone and Howard H. Talbot, llittsl'ourgh,l Pa.,

assignors, by mesne assignments, to Kelsey-Hayes Company, Detroit, Mich., a corporation of Delaware Filed Jan. 16, 1959, Ser. No. 787,173 8 Claims. (Cl. Sti- 16) This invention relates to an apparatus for cold forming principally by rolling of disks having a variable thickness contour such as are commonly used in the manufacture of heavy duty vehicle Wheels, harrow disks, and tur-bine and compressor rotor disks and the like.

A measure of success has been realized in the industry with respect to the production of disks having a given contour, attained by heating the blanks to a sufficiently high tempera-ture to permit them to be readily formed into the shape desired. -Disks produced by hot rolling, however, do not possess metallurgical properties necessary to meet critical requirements as are presently demanded. A number of methods and apparatuses, also, have been developed in recent years for the cold rolling or spinning of contoured disks, but none of them have been consistently able to produce disks which are wholly acceptable in all events fwith respect to smoothness of iinish or adaptability of being drawn vdirectly and without an intermediate edge annealing.

Some of the principal factors contributing to the failure of prior and existing contour disk rolling or spinning methods and apparatuses are: inherent deficiencies in the designs and construction of the mills; utilization of rolling or spinning reducing methods that are inherently incapable of effectively producing uniform marketable disks; failure to produce disks which could be directly formed by die forming or otherwise further formed without intermediate annealing to prevent edge splitting; failure to obtain proper cooperation between the metal reducing elements; failure to achieve uniform symmetrical manipulation of the metal reducing` elements Iwith relation to each other and to the blanks being reduced; difficulty of carrying out an operation due to intricate complicated apparatus available for the purpose; inability to obtain high effective rolling speeds; inability to make rapid changes, where changes are required, during the course of rolling in order to accommodate different sized disks and/or for the formation of dilferent contours, and the lack of effective automatic control of the many operating elements of the machines.

The present invention provides an apparatus for forming contoured disks in a highly economical manner, which, in addition to possessing many other advantages, overcomes each of Ithe aforementioned diiliculties and deticiencies inherent in existing disk rolling apparatus.

One of the objects of this invention is to provide for simultaneously forming a pair of variable thickness disks from a pair of untrimmed, constant thickness circular blanks by employing two pairs of cooperating reducing rolls, the rolling action as Well as the positioning and displacement of -which are so controlled that accurately rolled disks of pre-determined desired contours are assured.

Another object of this invention is to provide an apparatus for forming consistently uniform variable thickness disks eiciently and at a rapid rate of production.

It is another object of this invention to provide an apparatus for forming disks of a given contour in which two pairs of opposed cooperating rolls are diametrically arranged and adapted to be brought into a rolling relationship with a pair of blank disks positioned in a back to back relationship, the pairs of rolls being movable simultaneously in an axial outward direction.

It is still a further object of this invention to provide an apparatus for forming contoured `disks in which blanks are so rotated that the speed of the blanks at the initial point of contact is substantially equal t'o the peripheral speed of the reducing rolls, engaging and reducing the ydisks at two diametrically spaced points to provide a uniform taper from the point of first reduction to a point adjacent to the edges of the blanks.

It is still a further object of this invention to provide for the operational control of the apparatus disclosed herein wherein the rolls thereof may be operated at a constant speed while being withdrawn in an axial direction at a variable rate of speed or, alternately, ,the rolls may be rotated at a variable rate of speed and Withdrawn` axially at a constant rate of speed.

it is another object of this invention to provide adequate controls for the apparatus herein disclosed for rendering the apparatus fully automatic both for carrying out a single reducing operation as well as multiple re-1 ducing operations i.e., a single final reducing operation or at least one preliminary reducing operation prior to the nal one. j

It is still a further object of this invention to provide apparatus for rolling uniform contoured disks wherein the reducing rolls constitute a part of an assembly adapted to be directly and readily removed from an operative to an inoperative position for roll changing or for any other purpose without necessitating the use of auxiliary apparatus or the need for `disconnecting any elements from the assembly or the mill.

It is another object of this invention to provide a holddown member adapted to engage and rotate with a pair of `disk blanks supported by a spindle and accelerated to a speed substantially equal to the speed of the forming rolls at the point of initial contact, the spindle and the holddown member being so operable as to permit limited vertical movement of .the blanks :during a rolling operation.

It is another object of this invention to provide a mill for forming tapered disks in which the taper is controlled by means of complementary cams which may be quickly removed and replaced by others in a most highly eicient manner for changing the taper or forming a different contour on the disk.

It is another object of this invention to provide a disk forming apparatus adapted to perform either a one or a multiple of pass forming operations in which the rolls of the mill are vertically adjustable and the opening therebetween controlled to perform the operation desired.

These objects as well as the various other novel features and advantages of this invention will become apparent from the following description and accompanying drawings of whichr FIG. l is a plan View of a disk forming mill incorporating the features of and adapted to practice the method disclosed by the invention herein defined;

FIG. 2 is a front elevational View of the disk forming mill taken on lines II-II of FIG. l;

FIG. 3 is a partial sectional elevational side view taken at lines III-III of FIG. l;

FIG. 4 is a sectional elevational end View taken at lines IV-IV of FIG. 3;

FIG. 5 is an enlarged plan view of the right hand side of the mill shown in FIGS. l and 2; Y

FIG. 6 is an elevational view of the portion of the mill shown in FIG. 5;

FIG. 7 is an enlarged elevational View of the hydraulic control arrangement embodied in the mill shown in FIGS. 1, 5 and 6;

FIG. 8 is a plane View to designate the adjustable mill as shown in FIGS. 1 and 2.

3 control mechanism by which the traverse of the mill rolls is determined;

FIG. 9 is an elevational sectional view taken at IX-IX of FIG. 8;

FIGS l and l1 are enlarged sectional views of the holddown and disk supporting spindles respectively as employed in the mill shown in FIGS. 2 and 3, and

FIGS. l2 and 13 are an enlarged plan and front elevational views respectively of the screwdown arrangement employed in the disk forming mill as shown in FIGS. l and 2.

. With reference to FIGS. l and 2, there is illustrated therein a mill for forming disks which embodies the :features of the invention herein disclosed incorporating a rigidly constructed unitary housing 11 having T-shaped post sections =12 formed on the outside surfaces of two of the opposite sides thereof. The lower end-s of two sides of the housing terminate into pairs of spaced apart outwardly extending shoes 13 which rest upon individual parallel disposed bedplates 14, the bedplates being of suicient length to extend beyond the ends of the housing and being supported on suitable foundations provided for the purpose. Windows 15 are formed in the housing and centrally located in the opposite two sides thereof which are surrounded by the T shaped sections 12. In addition, windows 16 are also provided in the remaining opposite sides of the housing so that the configuration of the housing constitutes four vertical rigid posts joined together by thick top and bottom sections to form an integral unit.

With reference now to FIGS. 3 and 4, it will be appreciated that 4the elements illustrated therein having identifying numerals including the lower case letter b are identical to and symmetrically arranged with respect to other elements contained in the left hand portion of the Where the elements of the left hand portion of the mill are identidad, lower case letter a is included with the numerals.

In the upper and lower extremities of the housing 11 extending horizontally through the windows 15, lower and upper channel shaped cross-heads 17 and 18 are provided, the upper crosshead 18, when assembled in the housing, being arranged in an inverted position with respect to cross-head 17, as best shown in FIG. 4. The outer surfaces of the cross-heads are machine finished in order that they may be placed in a rigid contiguous .relationship with corresponding horizontal and vertical machine finished surfaces provided in the housing. After the cross-heads are placed in the windows 15, keys 19 vare wedged between the top and bottom of the mill housing and the horizontal projections Z1 provided on the cross-heads so that the cross-heads and the housing are rigidly connected together and act as an integral unit.

fThe cross-heads, as indicated in FIG. 3, extend beyond the ends of the housing for supporting other component parts of the mill which will be described hereinafter.

The four inside at surfaces of the web portions of the channel shaped cross-heads 17 and 18 that extend within the windows 15 are provided with a raised central portion having centrally located grooves or guides 22 into which there are received complementary projecting portions of two pairs of corresponding wedges 23h and 2417. These wedges are supported along their entire length within the housing and the width thereof corre- -sponds to the width of the raised central portions of the cross-heads and are Vso arranged that the narrow ends thereof will extend towards the vertical centerline of the mill. The lower Wedge element 2319, as shown in FIG. 4, is prevented from moving longitudinally by key 25 which is positioned in transversely arranged keyways provided in both the wedge and the lower cross-head. The upper wedge 24b, in contrast to the wedge 23h, is permitted to move in a horizontal direction in the guides 22 within the cross-head. This horizontal movement is accomplished by an individual high pressure piston cylinder assembly'26b connected tothe outboard end of the wedge and secured to and supported by a sliding casting 27h, the particulars of which will be described hereinafter. The upper wedge 24b and the piston cylinder assembly 2Gb will, for convenience, at times be referred to as the pass ditference wedge and cylinder. Each of the wedges 23h and 24b have a centrally located groove 28 provided on the inclined surface thereof into which there is received a complementary projection provided on the inclined surfaces of other wedges 3112 and 32h respectively which, though of the same width as the wedges 23h and 24?), are somewhat greater in length. The ends of the wedges 31b and 32h which extend away from the mill are connected to individual high pressure piston cylinder assemblies 33b and 34b respectively by which the Wedges are moved horizontally to effect vertical displacement of the rolls. The piston cylinder assemblies 33b and 346, as shown in FIG. 3, are mounted on suitable trunnions on extended portions of the cross-heads so as to permit the piston cylinder assemblies to pivot during operation. These wedges 31b and 32b and their respective piston cylinder assemblies 33h and 34h will, for convenience, at times be referred to as the pass clearance wedges and cylinders.

Engaged with the horizontal flat surfaces of wedges 31b and 32h there are two cam holders I3512 and 36b, the lower holders 35h, as best shown in FIG. 4, being inverted with respect to holder 36h. The holders are restrained `from moving transversely and longitudinally by suitable vertical guide surfaces provided on the crossheadS. By this construction, the cam holders are permitted to move vertically only. Into the open sides of the holders 35h and 36b, wedge shaped cams 37b and 38b respectively are received, these cams being shorter in length than the opening in the holders in order to facilitate ease of assembly. The cams are held in their proper positions in the holders relative to the centerline of the mil-1 by jack bolts G9. It will be observed that in FIG. '3 at shim plates 41 have Ibeen interposed between the horizontal adjacent inner surfaces of the holders and the cams.

The upper assemblies comprising the Wedges 24b and 32h, holders l36in and cams '38h are supported by balance assembly 40 having suitable hooked rods which extend down through the housing and top cross-head 18 and engage the projections extending outward from the cams as best shown in FIG. 4. The rods of each balance unit are connected together, see FIGS. 4 and 12, at the top of the housing by a common bar 50, the center of which is connected to the rod of a piston cylinder assembly 40b. The top cross-head 18 is provided with stop plates 51 which are arranged to be engaged by the earn holder Bob for supporting both the holder Iand the Wedges when these elements are lowered by releasing the pressure within the piston cylinder assembly 4Gb. When this takes place and after the jack bolts 39 are loosened, the cams continue to move down with and to the extent of travel of the rods and separate themselves from the cam holders. The weight of the wedges 2415 and 32k and cam holder 36h are then supported by the stop plates 51 so that the cam 38!) and/ or the shims 41 may be quickly and ediciently removed from the mill for replacement when necessary after the rolls have been withdrawn as will be discussed hereinafter. Removal `and replacement of the cams 37b and/:or shims 41 of the lower assembly may be readily accomplished manually after loosening the jack bolts 39 associated therewith.

It is `also to be appreciated that when the rolls are machined to restore the proper rolling faces thereof, a small decrease in diameter is compensated for by adjustment of the screwdown to be hereinafter described wherelas for a large decrease in diameter or rolls having a smaller diameter than those they replace by simply adding one or lmore suitable shims 41 between the cams and the holders thereby to re-establish the range of setting for the roll openings. Furthermore, Vsimply by inserting tapered shims as may be required, disks of a different angle of contour may be produced without requiring a multiplicity of expensive cams having a variety 'of angles of contour.

Extending between the pairs of cams 37b and 33h and arranged in the same vertical pl-ane, also as shown in FIG. 3, there are located in each window one pair of individual chock assemblies 42b and 43b, the chocks being arranged on opposite sides of the horizontal center-line of the mill. The chocks are made in the form of hollow tubular castings, the inboard ends being in the form of heavy rectangular sections having straight vertical sides corresponding to the sides of the housing post as best seen in FIG. 4. The vertical surfaces of the chocks are separated from the housing posts by liners 44 and housing liners '45. In addition, shim packs 46 are also shown to be inserted at one side of the chocks, a portion of which may be transferred to the other side of the chocks if it is desired to shift the chocks, the pair shown in FIG. 4 toward the rear of the mill, for example, and those of the other half of the mill, which are not shown in detail, by an equal distance toward the front of the mill. By offsetting the chocks in this manner the planes containing the axes of each pair of cooperating rolls will be parallel to each other and offset on either side of a parallel plane passing through the vertical centerline of the mill. The advantage resulting from this feature will be more fully discussed hereinafter.

Each of the chocks incorporate spaced apart roller bearings 47 and 48 which rotatably support longitudinally extending `shafts 49h and Sib. The bearings 47 are of lheavy duty type, as indicated in FIG. 3, in order to support adequately the overhanging load imposed during rolling upon the inboard ends of the shafts. In the vertical plane containing the large bearings 47 and on the sides of the chocks farthest away from the horizontal centerline of the mill, the chocks are vertically extended and in the extended portions thereof annular recesses are provided 'for receiving bearings 52 which rotatably support the journals of cam rollers or followers 54h and SSb. 'Ihe axes of the cam rollers 54h and 55h -are arranged at right angles to the axes of the :shafts 49b and Sib. The bearings 52 are maintained in their proper location by bearing caps 56 which are attached to the chocks by bolts or other sutiable fastening means. It is apparent, from FIG. 3, that the cam rollers 5415 and 5511 are adapted to rest on and travel over the cams 37b and Sb, the cams being made sufficiently long to provide a rigid backing-up support for the cam rollers during a disk for-ming operation.

At the outboard ends of each chock 4217 and 43]; there are two extensions 57]: and the extensions of the two chocks @2b and 43]) are pivotally connected together by a pin Sb secured to spindle support sta-nd 59b arrange-d at the ends of the shafts 49]) and Slb. The axis of the pivot establishes the horizontal pass line or centerline of the mill. This pivotal arrangement permits the rolls to be moved vertically toward and away from each other. A pair of piston cylinder assemblies Sib is arranged at the roll end of the lower chock assembly 42h, as best shown in FIG. 4, with the ends of the pistons thereof engaged with the lower surfaces of `the upper chock assembly 43b and by which means the top chocks are supported and the cam rollers 54h and SSb held against the ycams 37b and 3811 respectively. The spindle stand 5% is arranged between the outer ends of the shafts49b and Sib and the motor 62b, as best shown in FIGS. 5 and 6, the stands supporting the pivoted outboard ends of chocks 4219 and 43h and being provided with spindle supporting arms, not shown, which may be engaged with the driving spindles 63h and 64b when it is necessary to disconnect the lspindles from the ends of the shafts. Provisions are also made for moving the spindle stands transversely along suitable guide keys in order to maintain proper alignment of the roll shafts when the chocks are offset by transferring pontions of the shim packs 46 las explained heretofore. To facilitate this operation, jack bolts 651), as shown in FIG. 6,` are provided. The outer ends lof the shafts 49b and 51b are conneeted by universal couplings 66b `and 67h through the spindles 63h `and 64b to extension couplings 6811 and 69b respectively to the output side of a common gear drive 7Gb. The motor 62b is connected to the input shaft of the gear drive 7Gb.

To the enlarged inboard ends of shafts 49b and Slb, which extend beyond the ends of the chocks 42h and 43]), as shown in FIG. 3, there are affixed by means of suitable countersunk bolts and removable taper sleeves and keys, two cooperating large diameter relatively narrow width contour forming rolls 71h and 72b.

Similar platforms 73a and 73b are provided on each side of the mill, as shown in FIGS. l, 2, 5 and 6, and to which there are secured respectively spindle stands 59a and 59h, gear drives 70a and 7Gb and motors 62a and 62b. The platforms 73a and 73b `are mounted for longitudinal slidable movement upon suitable guides 74a and 74h respectively, as shown in FIGS. l and 5, affixed to sub-platforms 75a and 75b. As best shown in FIGS. l, 2. and 6, by means of connecting members 76a and 76b, and bedplates 14, `the sub-platforms 75a and 75h are fixed rigidly relative to the main mill housing 11. To the sub-platform 75a there is attached a double acting extended long stroke piston cylinder assembly 77, the piston rod 78 of which extends in a direction away from the mill and secured by a bracket 79 to the outer end of the platform 73a. Beneath the platform 75a and secured to -a bracket 80 which extends downward from platform 73a, there is 'attached an equalizer tension rod Sl which passes beneath the mill in a direction toward the other platform 75l). Secured to the other end of the rod S1 there is a rack 82, see FIGS. 2 and 6, the teeth of which are formed on the upper sides thereof. Rotatably secured to .the lower portion of the su-b-platform 75l), there'is a roller 83 which acts to guide and support the rack S2 'as it is moved longitudinally. Engaged with the teeth of the rack `82 there is an idler pinion 84 which is also rotatably secured to .the sub-platform 75b. Beneath the platform 73h there is also a rack 85, the teeth of which are on the lower side thereof and in mesh with the teeth of the-pinion 84. Thus, by this equalizing arrangement, when the platform 73a is moved outward to the left on 'actuation of the piston rod 78, the platform 731) will also -be moved outward for the same distance but in a direction to the right.

Inasmuch as the sub-platforms 75a and 75b are mounted over a pit provided in the foundation, retractable floor plates 86a and Stib are provided as a safety measure for keeping the pit covered during normal operation of the mill. The floor plates 3651 and 86h are pivotally connected -to the sub-platforms 75a and 75b and by means of suitable linkage to lthe platforms 73a and 73b respectively. The linkage is so arranged that there is suiiicient loose motion provided, thereby permitting movement of the platforms 73a and 73'b as is required for normal operation `of the mill. However, when it becomes necessary to ychange rolls, cams or shirns, then the platforms 73a and '13b are moved to their extreme left and right hand positions respectively which will cause the floor plates to assume the dotted line position as shown in FIG. o.

With reference to FIGS. 2 and 3, when the roll assemblies are retracted from the mill for' the purpose of removing tand replacing rolls, cams and shims, for supponting the chock and roll assemblies outward of the mill housing there are provided two pairs of parallel rails 87a and 87h which are secured to the sub-platforms '75a and 75h respectively, the mill ends of the rails being adjacent to the mill housing windows l5 and to the ends of the cams 37a and 37b and supported and guided on the bottom cross-head 17. The elevation of the inboard end of the rails is adjustable to compensate for the change in elevation of the lower cam rollers when the cams associated therewith are raised by insertion of shims to compensate for reduction in mill roll diameter caused by dressing the rolls. Inasmuch as the action is the same for yboth roll assemblies, for purposes of illustration, reference is made to FIG. 3 which illustrates the roll assembly of the right hand portion of .the mill. As the roll assembly is retracted, the cam roller 54h on passing over the end of the cam 37b, will pivot downward about the outer corner of the cam thereby to permit the assembly to be slowly lowered to deposit the bearing caps 56 upon the rails 87b. VOn further outward movement of the assembly, the bearing caps S6 will slide along the rails and thus alford continuous suppont therefor. The retraction of the mill roll assemblies to their most outward inoperative positions is eiected by opening a manually operable valve 90 which bypasses huid around the hydraulic system of control-s, thereby permitting the piston cylinder assembly 77 to travel beyond its outward normal position of operation.

With reference to the screwdown arrangement incorporated in the disk forming mill, the features thereof are shown particularly in drawings FIGS. 1, 2, 3, 12 and 13. As was previously mentioned, the pass clearance wedges 31b and 32h, FIG. 3, are connected .to the piston cylinder assemblies 33h and 34h respectively and are so arranged as to be moved into one of two positions, which positions correspond to the fully extended and to the fully retracted positions of the pistons of the cylinders and denes the roll open position and the roll closed position respectively. The pass difference wedge 24h, however, is movable and maybe stopped at any point intermediate its :two extreme positions, dependent upon the setting of a stop nut gear 9112.

As best shown in FIG. 3, the stop nut gear 91h is threaded on the piston rod of the pass difference cylinder.

Z6b and meshes with a splined gear 92b rotatably mounted in the upper extended portions of the upper cross-head 18. As the gear 92b is rotated, the gear 9111 will be caused to travel along the threaded rod. The cylinder 26h is secured to the lower portion of casting 27h, which casting is slidably supported in cross-head 1S and actuated by a cylindrical nut contained therein and \thread ably engaged with a rod 93h. Thus, depending upon the direction in which the rod 9'3b is rotated, the casting 271) and the cylinder 2Gb secured thereto will be moved in a direction toward or away from the mill.

Extending downward from the casting 27h there is a projection including an aperture 94h through which the rod of the pass difference cylinder 2Gb passes. Secured to the end of the casting 27b and adjacent to the stop nut gear 911:, there is a stop plate 95b provided for the purpose of limiting the movement of the gear 9117 on actuation of the cylinder 26b thereby to establish the rst pass roll opening for the mill rolls when the mill is to be operated on a two pass cycle. The rod 93b is journaled at both ends in the cross-head 1S, with the outer end thereof projecting through a crossahead end plate 96h and having a gear 97h keyed thereto, FIGS. 3, 12 and 13, which is rotated to be described thereby to move the casting 27b and the cylinder 2Gb and wedge 2417 as a unitV in a direction toward and away from the centerline of the mill. This results from the conditions that the cylinder 26h is constantly under pressure so that movement of the casting 27h will result in a corresponding movement ofthe wedge 24h.

As shown in FIG. 12, there are gears 98a and 98b which are operably connected to a common shaft 99 which, in turn, is connected to a motor 101 through a gear reduction unit 102, all of which are mounted upon mounting plates 100a and 100b which, in turn, are secured to the cross-head 18. To each end of the shaft 99, there are connected by miter gears 102m and 10311 finishing or second reduction pass setting screwdown indicators 104:1 and 104b. In addition, the mill screwdown arrangement includes a pass difference screwdown mechanism operably connected to a motor 105 through .a reduction unit 106, shaft 107 and two gears 1080 and 10817 which mesh with the two splined gears 92a and 92b respectively. Also there is a pass difference indicator 109 which is operably connected to the shaft 107 by miter gears 111.

As is shown in FIGS. l2 and 13, the three indicators 104s, 104K: and 109 are arranged on the operators side of the mill with the pass difference indicator 109 being located between the other two. The indicators 104:1 and 10417 are graduated in increments of .002 inch and .100 inch. By referring to these indicators, the operator is Venabled to set the proper opening between the mill forming rolls. For individually operating the screwdown on the left side of the mill relative to the other, a disengageaole clutch 112 is provided and is located on the shaft 99 between the two gears 98a and 98]; which may be engaged and disengaged by a manually operable lever 113 extending across the screwdown platform to a point between the indicators 104b and 109 so that it is readily accessible to the operator.

When the mill is being operated on a multiple roll pass as opposed to a single nal roll pass schedule, the pass difference indicator 109, which is graduated in .010 inch, is referred to for establishing the amount of reduction to be taken for the iinal pass. The reading on this indicator actually indicates when a two pass schedule is followed, the difference between the opening of the rolls for the preliminary reduction pass and the iinal reduction pass.

With reference to FIGS. 1, 3, 10 and 11, there is shown therein the spindle assembly 114 provided for supporting and for accelerating and decelerating the rotation of the disks prior to and after reduction of the blanks. This arrangement consists of a stem 115 having a hanged element 116 secured to the upperv end thereof upon which the disks rest when placed upon the spindle assembly 114. The lower end of the stem 115 is received in a recess provided in a cartridge 117, at the bottom of which recess there is positioned a compression spring 11S which yieldably engages the lower end of the stem 115. The cartridge 117 is rotatably received within an opening 119 formed in a casting 120 which is secured to the opposing four inside faces of the housing posts 12. Suitable bearings are provided on opposite ends of the cartridge within the casting 120. The lower end of the cartridge 117 extends beyond the lower face of casting 120 and is connected by a coupling 121 through a gear unit 122 to a motor 123, the motor 123 being shown in FIG. 1 and the coupling and gear unit being shown in FIG. 3. The stem 115 is keyed to the cartridge 117 in order to prevent relative rotation therebetween while permitting slidable vertical movement between the two. The ilanged element 116 is threaded on the upper end of the stem- 115 and is locked in position by an L-shaped key 124. The element 116 may be readily adjusted vertically by simply removing the key 124 and rotating the element to a point where the disk supporting flanged surface is at the desired vertical position. The stem 115 is free to move vertically during operation of the mill to the extent permitted by a long bolt 125 which is passed downward through the stem 115 and spring 118 and attached at its lower end to the cartridge.

With reference to FIGS. 3 and 10, holddown assembly 126 is shown therein and is mounted above and coaxial with the spindle assembly 114. The assembly 126 is slidably guided within an opening in a bracket 127 which is attached to the upper crosshead 1S. The assembly 126 consists of a plunger 128 slidable in opening 129 of bracket 127 and having secured to its upper end a piston rod 131 extending downwardly from a double acting cylinder 132 mounted on the top of the cross-head 18. With reference to FIG. 10, at the lower end of the plunger 128 there is a cavity 133 into which there is mounted a freely 9 rotatable shaft 134 supported therein by suitable bearings. The lower end of the shaft 134 has a flange 135 formed thereon which has a recess 136 therein adapted to be placed over the flanged element 116 of the spindle assembly 114. When a pair of disk blanks is positioned upon the assemblies, the anged element 116 and the flange 135 will engage the disks with su-fcient pressure so that on rotation of the spindle assembly 114 the disks will be accelerated to the proper speed so that the surface speed of the disks at the point where the rolls will first make contact with the disk will be substantially the same as the peripheral speed of the rolls before the rolling operation commences and decelerated to a standstill prior to removal of the completed disks from the mill. The pressure exerted by the cylinder 132 is so controlled that it will essentially balance the force exerted by the spring 118 after the disk blanks have been placed thereon.

As previously mentioned, the mill disclosed herein may be operated either at a variable rolling speed and constant roll withdrawal rate or at a constant rolling speed and a variable roll withdrawal rate. As will be determined by the operator, either rolling procedure may be readily practiced merely by making the required adjustments of the controls for accomplishing the purpose.

With reference first to the operation in which the forming rolls will be driven at a variable rolling speed and withdrawn at a constant rate of speed, attention is directed to FIGS. 5, 6, 8 and 9 of the drawings wherein the various elements for accomplishing this purpose are shown. On one side of the mill a vertical support 141 is secured to the stationary platform 75b which extends above the bottom surface of the movable platform 7315. The top of the support 141 is rectangular in shape and to the four corners thereof there are aflixed four limit switches 14251, 142.6, lil-2c` and 142g? having actuating rollers which project upward. To the side of the movable platform i311 there is secured an inverted L shaped support 143 which extends above and overhangs the stationary support 141. On the support 143 and at the upper portion thereof there are arranged in a horizontally spaced relationship four threaded shafts 14K-la, 144k', 144e and 144d, each having secured thereto a handwheel 145e, 145b, 145e and 145d respectively. Threadably mounted upon and adjustable in an axial direction relative to each of the shafts 144:1, 141th, 14d-c and 14E-4d there are individual cam blocks 146:1, 146]), 146e, and 146:1. Attached to the cam blocks there are individual pointers 147a, 147b, 147C and '14761 respectively all of which pointers are movable along a common scale bar 148 secured to the support 143. Although limit switch cam block relationships are not shown for all of the switches, in HG. 9 it is evident that cam block 146a will trip limit switch 142er, and cam block 146e will trip limit switch 142C. Similarly the other two cam blocks 146i) and 146e! will trip the remaining limit switches 14217 and '142:1 respectively.

As best shown in FiG. 8, both ends of the scale bar 143 are graduated in inches with the marks scribed on the edges of the uppersurface, the scribed edge portions being identified as first pass bite, second pass bite, first pass runoff and second pass runoff. On the left edge, the graduations are in increments of one inch and read from right to left 10 inches to 20` inches and these markings are so arranged that they apply to both the first and second roll pass bite positions. On the right end portion of the gage bar 148, the graduations are also in one inch increments and read from right to left inches to 30 inches and these markings apply to both the first and the second pass runoff positions, i.e., posi-- tions at which the forming rolls open. The numerals on the pass bite or left end portion of the scale bar represent the distance on a diameter of the disks that the rolling or reducing portion of the pairs of rollsv are spaced from each other, which spacing will be termed the bite circle. For example, the pointer y147b, as shown in FIG. 8, indicates that the bite circle for the first pass is set at 17 inches and the pointer 147e indicates that the second pass bite circle is set at l0 inches. The readings signify that where a two pass operation, as opposed to a single pass operation, is to be performed, for the nrst rolling pass the distances between the working or reducing points of the two pairs of rolls will be 17 inches at the time the rolling operation first commences and for the second rolling pass the distances between the working or reducing points of the two pairs of rolls will be 10 inches at the time the second or final rolling operation begins. Also as shown in. FIG. 8, the pointer 147d indicates that the forming rolls will be opened clear of the disks when they are 2.0` inches apart on a diameter for the first pass and that the rolls will be opened clear of the disks when they are 27 inches apart on a diameter for completion of the second pass operation. Thus, with the controls as defined, it is possible to open the rolls at any point on the disk prior to reaching t-he edge of the disks.

A third pointer 149, arranged centrally on the support 143, is adjacent to and registers with a scale bar 151 secured to the front of the stationary support 141. The scale bar 151 is Ygraduated in inch increments and reads from left to right from 9 inches to 30 inches. The position of pointer 149 along the scale bar 151 indicates to the operator at all times the diametrical spacing between the rolling points of the rolls.

At the lower end of the assembly, as is best shown `in FIG. 9, there is a tapered horizontal cam 152 which is pivotally mounted at its one end on the movable platform Sb and connected at its other end to an adjustable rod-nut assembly `153 secured to the platform 7311. The cam 152 corresponds in length to the radius of the largest disks which are to be formed on the mill. The lower or cam surface of the cam '152 is engaged by a roller 154- mounted upon the upper end of a plunger 155 which is housed in a guide 156, the plunger 155 being constantly urged in an upward direction. The plunger extends beyond the lower end of the guide and on a threaded portion of the lower end thereof there is an adjustable knurled nut 157. The lower end of the plunger 155 engages with the stem of an electrical saturable-core reactor 158 which, according to the vertical position thereof, determines the speed at which the motors 62a and @2b will be operated. When the roller 151i is in the position shown in FIG. 9, it is to be appreciated that the mill forming rolls will at the same time be in position for commencing a forming operation so that as the forming operation progresses, the cam 152 will move along the roller 154 and the plunger 155 will gradually rise so that the reactor 158 will cause the speed of the motors and hence the speed of the forming rolls to increase proportionally as the rolls are withdrawn outward on the disks. rPhe maximum speed of rolling is determined by the position of nut '157 with respect to the lower end of the guide 155.

With further reference to the elements employed in an operation in which a variable rolling speed is to be employed, the cam- 152 is adjusted by rotating the adjustable knurled nut of the rod-nut assembly 153 thereby to cause the cam 152 to pivot about its other end and thus to cause the plunger 155 to be raised or depressed for obtaining the desired rolling speed. Due to the location of the pivot point relative to the cam roller 154 and also to the fact that the length of the cam 152` is at least equal to the radius of the largest disk to be processed by the mill, the height of the cam 152 is proportional to the speed of rolling at that particular disk diameter represented by the position of the cam roller 154 on the cam 152.

With particular reference to FIGS. 5, 6 and 7, the elements will now be described which are employed for 11 operating the mill in such a fashion. that the rolls rotate at a constant speed and are Withdrawn radially at a variable rate of speed. FBhe hydraulic arrangement employed lfor the purpose consists ot three rhow control valves 159a, 15917 and 159C, the valves 159e and 159b being of equal dow capacity whereas the valve 159C is Yof substantially less capacity than the other two. These valves, together with an oriiice valve 159d are all connected in parallel to the piston cylinder assembly 7-7. The orifice valve 15911 is connected in series with and is controlled by an on-ol valve 160. For varying the rate of flow of uid delivered by the flow control valves 159g, 159b and 159e, there is connected thereto a common push rod 161 to which individual pointer elements 162a, 162b and 162e.` are operably connected. The pointer elements 162:1, 162b and 162e are also connected to the valve stems of Ithe respective valves 15961, 15911 and 159e. On movement of the push rod 161, the pointers thus not only will cause the valves to open or close to regulate the flow of uid therethrough, but will also indicate the extent of the opening by the position thereof relative to the scales associated therewith. At the right hand end of the rod 161 there is secured a spring 163 which constantly urges the push rod to its most extreme position to the right as shown in FIG. 7. To the opposite end of the rod 161 there is connected an adjustable length link 164 which is pivotally connected to a lever 165 by means of a locking adjustable pin 166 passed through a curved adjustment slot provided on the lever 165. The lever 165 is, in turn, keyed to one end of a shaft 167 to which there is also keyed an arm 168 having affixed to the outer end a -vertically extending threaded rod 169. The rod 169 slides within a suitable guide 171 and has a cam follower or roller 172 at its lower end which engages with the surface of a cam 173 secured t0 and extending outward from theV movable platform 73h. With the exception of the cam 173, the entire hydraulic control assembly is mounted upon asuitable bracket 174 secured to the stationary sub-platform 7517 on the operators side of the mill.

When the mill -is to operate at a constant rolling speed and at a variable withdrawal rate of the forming rolls, the operator determines the flow of uid required to cause the rolls to traverse the disks at the proper rate and opens the required number of shut oi valves, not shown, in order to permit lluid to iiow through the required valves 159er, 15912 and 159C. At the same time the operator will adjust the locking pin 166 to its proper position within the curved slot to cause the correct rate of ow to take place through the fow control valves v159:1, 159b and 159L` as will be indicated by the positions of the pointers 162a, 162b and 162e respectively. The rate of flow through the valves will be varied proportionally according to the position of the cam 173 with respect to the cam follower 172 as the cam and the reducing rolls are traversed outwardly with respect to the center line of the mill thereby to give a uniform traverse per revolution of disk. The position of the cam 173 with respect to the follower 172, as shown in FIG. 7, indicates the rela- 'tive position of the rolls with respect to the disk when the rolling operation is to commence and from which the withdrawal of the rolls will proceed by actuation of the piston cylinder assembly 77. As the reducing rolls are withdrawn, the cam follower 172 will pass over the cam 173 thereby permitting the follower to lower and lthe push rod `161 to -be actuated toward the right by the spring 162 as viewed in FIG. 7. Movement of the push rod 161 will cause the pointers 16211, 162b and 162C to turn counter-clockwise thus to reduce the rate of iluid ilow through the control valves as the reducing rolls are moved radially outward with respect to the disks. On

' completion of a reducing operation, the cam yblock 146 strikes and iactuates the second pass limit switch 142, which operates valve 16) thereby causing the orice valve 15Std to functionrto admit additional fluid to the piston cylinder assembly 77A thereby causing the reducing rolls to be withdrawn rapidly from the disks so that the finished disks may thereafter be readily removed from the mill.

On the other hand, when the rolls are to be withdrawn lat a constant rate, then the llow control valves' 159m 15% and 159C are adjusted manually by positioning the pointers 16211, 162b and 162e at the desired lo` cation to provide the required rate of ilow. This is accomplished by repositioning the 'locking pin 166 in the curved slot of the lever 165. By an adjustable nut 175, which is rotated until the follower 172 is lifted from the cam 173, the cam and follower are thereby rendered inoperative preventing displacement of the push rod 161.

Suitable loading and unloading devices 176 and 177 respectively are shown with the mill in FIG. l. The loading device 176 is so devised as to receive a pair of blank disks and place them upon the spindle assembly 114 for carrying out a reducing operation and the unloader 177 is operable to engage with the same pair of disks following a reducing operation for removing the tinished product from the mill.

Particular attention is now directed to certain features ot the present invention as related to the method of forming tapered disks from blanks of uniform thickness. As has been mentioned, it is a feature of this invention that the reducing .rolls are provided in pairs, 71a and 72a constituting one pair and 71b and 72b constituting the other pair. The pairs of rolls are arranged at diarnetrically opposite points equidistant from the vertical centerline of the mill or central axis of the disks to be reduced. For a normal rolling operation, the rolls are so positioned that the axes of both pairs are contained in a Common plane which passes through the centerline of the mill or central axis of the disks. It is an advantage of this mill that the rolls may -be `displaced away from 4the common plane and on opposite sides thereof so that the axes of each pair will be contained in new planes parallel to the common or original plane. Depending upon the rotation of the disks, the reducing rolls can be so positioned that the axes of the rolls Will fall ahead of or behind the original plane passing through the axis of the disks. By so doing, a radial lcomponent of force is crelated in the direction of or opposite to the direction of the force exerted to withdraw the rolls across the disk. When in a position ahead of the common plane, the rolls actually assist in the withdrawal action and thus aid the piston l'cylinder assembly 77. When the rolls are in the opposite positions with respect to the common plane, there are forces set up by the rolls which act in a direction opposite to that of the piston cylinder assembly 77. The most optimum condition for 4rolling can be attained merely by increasing or decreasing the distance between the axes of the reducing rolls and the original plane containing the axis of the disks. lIn order to olfset the reducing rolls, a suicient number of the shims of the shim packs `46 are simply removed from the right side and inserted on the left side of the chocks as shown in FIG. 4 and similarly removed from the left side of the chocks on the left side of the mill, which are not shown specilically and rcinserted on the right side of these checks. Thus, the offset required for a particular reducing operation may he readily accomplished.

Although some phases of operation of some of the elements comprising the invention herein defined have previously lbeen set forth, complete `operation of the entire apparatus with respect to the various features thereof will now be described in greater detail. Before actual operation of lthe mill takes place, however, there are certain adjustments which must be made in consideration of the material to be reduced, the taper to which the disks are to be rolled and the particular lsteps to be followed for carrying out the operation. It will be assumed that the proper cams 37a, 37b, 38a and b have been inserted in the mill, and if found to be necessary, shims 41 may be tapered to obtain the particular disk contour desired. The opera-tor then will set the iirst and second bite limit switch cam blocks idal and 146b in their proper relationship for establishing the exact radial positions at which the rolls will enga-ge the disks both for the rst and the second pass bite circles. ln addi-tion, the same adjustment is made with respect to the tirst and second pass runo limit switch cam blocks 146o and Mod. Should it be desired to operate the mill on a one pass cycle only, then the -iirst pass bite cam block 14611 and the first pass runoii ca-m block Med will have been so adjusted -that they will not interfere with the operation of cam blocks 146e and 146C when the reducing rolls traverse the disks.

Let it be assumed that the mill is to be so operated that the reducing rolls are rotated at a constant speed and that the rate will vary at which the rolls are Withdrawn radially of the disks during the rolling operation. The pre-selected constant rolling speed is established by proper setting of a suitable rheostat associated with the motors 62a and 62h. In order to provide the proper variable withdrawal rate, let it be assumed that the hydraulic system also requires adjustment. With the cam follower 172 in the position shown in FIG. 7 and the nut 175 spaced the proper distance from the guide 171, the required -ilow control valves 15%, 1595 and 159C will then be adjusted to provide the necessary low of iluid therethrough as previously determined by the operator to be required for the desired rate of withdrawal. The adjustment of the valves is accomplished by moving the locking pin 166 along the slot of the lever 165 until the pointers 162e, 162i; and 162C indicate the top limit of the ow range desired.

If the disks are to be subjected to a two pass as opposed to a single pass reduction, then the `operator will adjust the tinal pass screwdowns, the adjustment being shown on indicators i645: and 1Mb, to a point where the indicator readings correspond to the roll opening selected for the second pass for reducing the disks. By adjustment of these screwdo-Wns, the slidable castings 27a and 27h, the pass difference cylinders 26a and 26b and the pass `dierence wedges 24a and 24]) respectively, FIG. 3, will move to -their proper pre-selected positions. inasmuch as the piston ends of the cylinders lare under a constant pressure, the stop nut gears 91a and 91h are held away from the stop plates Sa and 95h. On accomplishment of this adjustment, the pass difference screwdown will then be operated to cause the stop nut 91b and also ythe stop nut corresponding thereto on the left side of the -mill to move away from the stop plate 95]; and the stop plate on the opposite side respectively thereby lto permit the wedges 24b to travel the required distance to the right and the correspond-ing wedge on the left side of the mill to the left to establish the roll position for the first pass. The screwdown indicator 109 will then indicate the reduction which will be taken on the second pass, the second pass bite cir-cle beginning radially inward of the tirst. By proper adjustment of the motor i231, FIG. l, the speed of the stem 115 will be so established that when either a single pass operation is performed or the second pass `of a two pass operation is being carried out the speed of the disks will be substantially the same as that of the rolls when the rolls -tirst make contact with the blanks.

After the mill has been -set up in accordance with the foregoing, it is now in readiness for operation. To load the mill, a pair of blank disks, in back to back relationship, is placed upon the loading device 176, FIG. 1, which is actuated to deposit the disks upon the spindle assembly 114, after which the holddown device 126 is rnoved vertically downward to engage the disks and press themr firmly against the flanged element lll so that the friction between the two will be sutlicient to prevent slipping of one relative to the other and then the disks are accelerated to the speed desired. Since the reducing rolls of the mill are in their most extreme withdrawn position, the rolls, of course, will be open inasmuch as the pass clearance wedges Sib and 32b on the right side of the mill as well as the corresponding ones on the left side of the mill will be in their inboard or roll open positions. Pressure is then applied to -cylinder 77 to cause the rolls to pass inward toward the center of the mill with the disk blanks therebetween. The inward movement thereof will be interrupted when the rst pass limit switch 142!) is tripped on .being engaged by the cam block 14619. The cam block and the tirst pass limit switch may fbe `so related that the reducing rolls may either vbe permitted to over travel inward beyond the rst bite circle or inward movement of the rolls may be interrupted at :the bite circle where rolling is to begin.

As soon as the rst pass limit switch 1421; is tripped, fluid is admitted to the piston cylinder assembly 77 yfrom its opposite end thereby to cause the reducing rolls to be withdrawn radially outward. At the same time, but prior to lactual withdrawal of the rolls, if the rolls are then actually positioned adjacent to the points at which they -are to make rolling contact with the rolls, the pass clearance cylinders 33h and Mb and those on the left side of the mill will be operated to close the wedges Slb and 32h and also the corresponding wedges on the left side of the mill thereby to cause the vrolls to make contact with the disks and reduce the disks on a taper as the pairs of rolls are simultaneously withdrawn outward during the iirst pass. On movement of the rolls outward, the cam block 14M will trip the rst pass runoi limit switch .1.42ct which will cause the pass clearance cylinders 33t) and 34h and the corresponding ones of the left side of the mill to be actuated thereby to open the wedges 3lb and' 32h and those on the left side so that the reducing rolls open also. At the same time, the oriiice valve 159e will be `opened on operation of the control valve 16).

The foregoing action also causes tluid to be again introduced to reverse direction of the piston cylinder assembly 77 so that the movement inward of the reducing rolls will move quite rapidly inwardly by reason of the fact that the orice valve 159e? is not interrupted until the second pass operation commences. Tripping of the rst pass runoif limit switch 14261 also causes the pass difference cylinders 26a and Zeb to be actuated thereby to move the pass difference wedges 24a and 24b and by which the stop nut gears 91a and 91]; are moved away `from the stop plate 95a and 95h thus to close the rolls at their second pass positions. Inasmuch as the pistons in the cylinders abut against the piston end of the cylinders, further movement of the Wedge Zdb and the corresponding wedge on the left side of the mill is prevented.

As the rolls move in across the disks to perform the second pass reducing operation, the cam block .Moa will trip the second pass bite circle limit switch 142a which will cause the pass clearance wedges 3l!) and B2b and the corresponding ones on the left side of the mill to close thereby closing the rolls. At the same time the orice valve 15.15%' is closed and the piston cylinder assembly 77 is reversed to cause the reducing rolls toV be withdrawn radially outward of the disks to complete the second pass reducing operation.

Following the tripping of the second pass runoi limit switch 142e by the cam block 145C, the reducing rolls on completion of the reducing operation and before they are permitted to pass over the edges of the disks are opened and rapidly withdrawn beyond the edges of the disks where movement is interrupted by a suitable time delay limit switch incorporated in the electrical control system. The spindle assembly 114 is then quickly decelerated and the holddown device 126 raised to permit the unloading device 177, FIG. 1, to engage the disks and remove them from the mill.

Although the drawings for purposes of illustration show a pair of blanks as being simultaneously processed in the mill disclosed herein, it is to be appreciated that the apparatus may be employed for processing one or more disks at the same time and, `if necessary, any number of preliminary reducing operations may be taken as conditions may dictate.

In accordance with the provisions of the patent statutes, we have explained the principle and operation of our invention and have illustrated and described what we consider to represent the best embodiment thereof. However, we desire to have it understood that within the scope of the appended claims, the invention may be practiced other-wise than as specifically illustrated and described.

We claim:

1. A mill for cold rolling blanks to form disks of a desired contour comprising a fixed housing having at least two vertically extending windows in the opposite sides thereof, a pair of vertically disposed checks on either side ofthe vertical centerline of the mill and arranged for horizontal and relative vertical movement within each of said windows, a shaft rotatably supported by each of said chocks, a reducing roll secured to the end of each of said shafts adjacent to said chocks, means engaging at least one of the chocks of each pairs and said housing so arranged to provide a rigid construction between the housing and chocks during the rolling operation and operable to displace said chocks and rolls associated therewith in a vertical direction, means operatively connected to and for displacing said pairs of chocks and rolls in a horizontal direction, means connected to said pairs of checks to cause simultaneous movement therebetween an equal distance with respect to the Vertical centerline of the mill, the extent of said horizontal displacement being related to the relative vertical displacement of said chocks thereby to effect the desired contour and means connected to and for driving said shafts and the reducing rolls connected thereto.

2.l A mill for cold rolling blanks according to claim l in which said chocks are adapted to be adjusted transversally within said windows, and means are provided for maintaining said chocks in their transversally adjusted positions.

3. A mill for cold rolling blanks to form disks of a given contour comprising a xed housing having at least two vertically extending windows in the opposite sides thereof, a pair of crossheads with one above the other extending through said windows and secured to said housing, a pair of vertically disposed chocks arranged for horizontal and relative vertical movement within each of said windows, said pairs of chocks being symmetrically arranged with respect to the centerline of the mill, a shaft rotatably supported by each of said chocks, a reducing roll secured to the end of each of said shafts adjacent to said checks, a cam and follower operatively arranged between each chock of the upper pair and the upper crosshead so arranged to provide a rigid` construction between the housing and said shaft during the rolling operation, means operatively connected to and for displacing said rolls on either side of the vertical centerline of the mill thus to displace said cams and vfollowers relative to each other thereby to define the opening between the reducing rolls during a reducing oper-ation, means for causing simultaneous movement of said pairs of rolls an equal distance with respect to the vertical center line of the mill and means connected to and for driving said shafts and the reducing rolls connected thereto.

4. A mill for cold rolling to form disks of a given contour comprising a fixed housing having at least two vertically extending windows in the opposite sides thereof, a pair of cross-heads one above and one below extending through said windows and secured to said housing, first upper and lower wedge elements, said upper wedge ele- Y ments with the inclined surfaces thereof facing in a downward direction and slidably received in said upper crosslo head, said lower wedge elements with the inclined surfaces thereof facing in an upward direction secured to said lower cross-head, a complementary wedge element in Vslidable engagement with each of said upper and said lower wedge elements, upper and lower cam holders operatively engaged with said ycomplementary wedge elements and restricted to move in a vertical direction, a cam secured to each of said holders with the cam surfaces thereof facing in a direction toward the horizontal centerline of the mill, a pair of chocks arranged for horizontal and relative vertical slidable movement within each of said windows, said pairs of checks being symmetrically arranged with respect to the vertical centerline of the mill, a shaft rotatably supported by each of said checks, a reducing roll secured to the end of each of said shafts adjacent to said chocks, a cam follower secured to each of said shocks, yieldable means urging each of said cam followers into engagement with said cams, an arm extending outward from said chocks in a direction away from the vertical centerline of the mill and intersecting the horizontal centerline thereof, the arms on either s-ide of the vertical centerline of the mill constituting a pair, means pivotally connecting each pair of arms together on the horizontal centerline of said mill, means interconnecting sa-id last mentioned means and operatively yarranged to displace said pairs of rolls in a horizontal direction away from each other an equal distance with respect to .the vertical centerline of the mill and to cause said cam followers to traverse said cams thereby to define progressively the opening between the reducing rolls dur-ing a rolling operation, and means connected to and for driving said shafts and the reducing rolls connected thereto.

5. A mill for cold rolling blanks of a constant thickness to form disks of a radially varying thickness comprising a fixed housing, first wedge elements arranged in vertically spaced relationship in the upper and lower portions of said housing, a complementary wedge element slidably engaging each of said first wedge elements, two pairs of vertically disposed chocks slidably arranged within said housing, a shaft rotatably4 supported by each of said chocks, the two reducing rolls associated with each pair of checks defining a blank reducing pass, a cam and follower operatively yarranged between each of said chocks and said housing, means for driving said shafts, means connected to and for displacing said complementary wedge elements, means connected to and for displacing said first wedges mounted in the upper portion of said housing, adjustable stop means engageable with and for determining the extent of displacement of said last mentioned elements and means operatively connected to and for moving said rolls in a horizontal direction radially across said blanks and for displacing said cams and followers relative to each other thereby to define progressively the opening between the rolls and the extent to which said blanks are reduced.

6. A mill for cold rolling metallic blanks to form disks of a given contour comprising a fixed housing having at least two vertically extending windows in the opposite sides thereof, Ia pair of cross-heads with one above the other extending through said windows and secured to said housing, first upper and lower wedge elements, said upper wedge elements with the inclined surfaces thereof facing in a downward direction and slidable within said crosshead, said lower wedge elements with the inclined surfaces thereof facing in an upward direction secured to said lower cross-head, a complementary wedge element in slidable engagement with each of said upper and said lower wedge elements, means connected to and for displacing each of said upper and lower wedge elements relative to said complementary wedge elements slidably engaged therewith, adjustable stop means operatively arranged to determine the extent of the displacement of said upper wedges, upper and lower cam holders loperatively engaged with said complementary wedge elements and restricted to move in a vertical direction, a camsecured to each of said holders with the cam surfaces thereof facing in a direction toward the horizontal centerline of the mill, two pairs of vertically disposed chocks arranged for horizontal and relative vertical slidable movement within said windows, a cam follower secured to each of said chocks Iand in engagement with said cams, said pair of chocks being symmetrically arranged with respect to the vertical centerline of the mill facing each other and positioned co-axiaily with respect to each other on opposite sides of the vertical centerline of the mill, la shaft rotatably supported by each of said chocks, a reducing roll secured to the end of each of said shafts adjacent to said chocks, yieldable means urging each of said cam followers into engagement with said cams, an arm secured to each of said chocks and extending in a direction away from the vertical centerline of said mill and intersecting the horizontal centerline thereof, the arms on either side of the vertical centerline of the mill constituting a pair, separate means pivotally connecting each pair of arms together on the horizontal centerline of said mill, means interconnecting said last mentioned means and operatively arranged to displace simultaneously said pairs of arms in a horizontal direction away from each other an equal distance with respect to the vertical centerline of the mill and to cause sa-id cam followers to traverse said cams thereby to define progressively the opening between the reducing rolls during a rolling operation, means connected to and for driving said shafts and the reducing rolls connected thereto, a rotatable spindle for supporting and centering said blanks in said mill, and means connected to and for rotating said spindle.

7. A mill for cold rolling Workpieces comprising a housing having a vertically extending window formed therein, an assembly including a pair of vertically disposed chocks normally positioned within said window, a shaft rotatably supported by each of said chocks, a reducing roll secured to one end of each of said shafts and means interconnecting each of said checks, means for effecting relative vertical movement of said chocks, including a cam element and a follower element in contact therewith of which elements one is secured to said housing and the other secured to one of said checks, a support adjacent to and extending outward from said housing in a substantial horizontal direction, and means connected to and for retracting said assembly directly from an operative to an inoperative position clear of said housing along said support and without disturbing the adjustment of said Erst-mentioned means thereby to permit ready removal and replacement of said rolls and adjustment and replacement of said elements.

8. A mill for cold rolling blanks to form disks of a given contour comprising a xed housing having a vertically extending window therein, a pair of vertically disposed chocks arranged for horizontal and relative vertical ymovement within said window, a shaft rotatably supported by and projecting beyond the body of each of said chocks, a reducing roll secured to the projecting ends of each of said shafts, means connected to and for moving said chocks in a horizontal direction in said window, contour establishing means rigidly engaging said chocks and said housing adapted upon operation of said mill to transmit pressures due to rolling directly from said chocks to said housing.

References Cited in the tile of this patent UNITED STATES PATENTS 1,004,771 Gibbons Oct. 3, 1911 1,430,989 Heisler Oct. 3, 1922 1,534,860 Martin Apr. 2l, 1925 2,280,783 Bell et al. Apr. 28, 1942 2,338,161 Ashton Ian. 4, 1944 2,588,651 Nelson Mar. 11, 1952 2,647,422 Horn Aug. 4, 1953 2,775,152 Krause Dec. 25, 1956 2,894,422 Hautau July 14, 1959 2,932,223 Chartrand et al Apr. l2, 1960 FOREIGN PATENTS 776,227 Great Britain June 5, 1957 

1. A MILL FOR COLD ROLLING BLANKS TO FORM DISKS OF A DESIRED CONTOUR COMPRISING A FIXED HOUSING HAVING AT LEAST TWO VERTICALLY EXTENDING WINDOWS IN THE OPPOSITE SIDES THEREOF, A PAIR OF VERTICALLY DISPOSED CHOCKS ON EITHER SIDE OF THE VERTICAL CENTERLINE OF THE MILL AND ARRANGED FOR HORIZONTAL AND RELATIVE VERTICAL MOVEMENT WITHIN EACH OF SAID WINDOWS, A SHAFT ROTATABLY SUPPORTED BY EACH OF SAID CHOCKS, A REDUCING ROLL SECURED TO THE END OF EACH OF SAID SHAFTS ADJACENT TO SAID CHOCKS, MEANS ENGAGING, AT LEAST ONE OF THE CHOCKS OF EACH PAIRS AND SAID HOUSING SO ARRANGED TO PROVIDE A RIGID CONSTRUCTION BETWEEN THE HOUSING AND CHOCKS DURING THE ROLLING OPERATION AND OPERABLE TO DISPLACE SAID CHOCKS AND ROLLS ASSOCIATED THEREWITH IN A VERTICAL DIRECTION, MEANS OPERATIVELY CONNECTED TO AND FOR DISPLACING SAID PAIRS OF CHOCKS AND ROLLS IN A HORIZONTAL DIRECTION, MEANS CONNECTED TO SAID PAIRS OF CHOCKS TO CAUSE SIMULTANEOUS MOVEMENT THEREBETWEEN AN EQUAL DISTANCE WITH RESPECT TO THE VERTICAL CENTERLINE OF THE MILL, THE EXTENT OF SAID HORIZONTAL DISPLACEMENT BEING RELATED TO THE RELATIVE VERTICAL DISPLACEMENT OF SAID CHOCKS THEREBY TO EFFECT THE DESIRED CONTOUR AND MEANS CONNECTED TO AND FOR DRIVING SAID SHAFTS AND THE REDUCING ROLLS CONNECTED THERETO. 